CN101021255B - Multi-gear transmission - Google Patents
Multi-gear transmission Download PDFInfo
- Publication number
- CN101021255B CN101021255B CN200710005337.1A CN200710005337A CN101021255B CN 101021255 B CN101021255 B CN 101021255B CN 200710005337 A CN200710005337 A CN 200710005337A CN 101021255 B CN101021255 B CN 101021255B
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- Prior art keywords
- clutch
- planetary gear
- multispeed manual
- axle
- gear set
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention relates to a multi-gear transmission provided with six forward gears and a reverse gear. The transmission comprises an input shaft (1), an output shaft (2), three planetary gear sets (P1, P2, P3), six rotating shafts (1, 2, 3, 4, 5 and 6) and five gear change components (03, 04, 13, 14 and 36). The input shaft (1) is connected with the central gear of the second planetary gear set (P2) all the time, with the shaft (3) through a clutch (13), with the shaft (4) detachably through a clutch (14). The shaft (3) is connected with the connecting piece of the first planetary gear set, is connected to an encloser (G), and with the shaft (6) detachably through a clutch (36). The shaft (4) is connected with the central gear of the first planetary gear set (P1), and is connected to the encloser (G). The shaft (5) is connected with the inner gear of the first planetary gear set (P1) and the connecting piece of the third planetary gear set (P3) all the time. The shaft (6) is connected with the inner gear of the second planetary gear set (P2) all the time. The output shaft (2) is connected with the inner gear of the third planetary gear set (P3) and the connecting piece of the second planetary gear set (P2) all the time. The central gear of the third planetary gear set (P3) is connected to the encloser (G) through a shaft (0) in a torsion resistant way.
Description
Technical field
The present invention relates to a kind of multispeed manual transmission of planetary gear construction, particularly a kind of by the described automatic transmission for automobile of claim 1 preamble.
Background technique
Particularly the automatic transmission of automobile comprises planetary gear set according to prior art, and they are by for example being connected friction or the gearshift parts connect and usually for example be connected as fluid torque converter or hydraulic coupling with the activation member of bearing the slip effect and be connected with selectivity the tap clutch with break as clutch.
This speed changer is open by EP 0 434 525 A1.It consists essentially of input shaft being set parallel to each other and output shaft, one with the compound planet gear group of the concentric setting of output shaft with five gearshift parts of three clutches and two break modes, and selectivity is closed in couples separately determines variator drive ratio different between input shaft and the output shaft for they.This speed changer has a preposition gear train and two power paths in this case, thereby paired in conjunction with realizing six forward gears selectively by five gearshift parts.
In this case, need two clutches at the first power path, be used for two parts transmitting torques from preposition gear train to the compound planet gear group.These parts are arranged on the preposition gear train back that the compound planet gear prescription makes progress basically on the power transmission direction.Be provided with another clutch at the second power path, it can be connected this power path dividually with another parts of compound planet gear group.Clutch arranges so in this case, makes the inner attrition piece support form output member (Abtrieb).
In addition, US 6.139.363 discloses a kind of compact type multispeed manual transmission of the planetary gear construction especially for automobile, has two planetary gear set and preposition gear train and three clutches and two breaks.In disclosed this multispeed manual transmission, have two clutch C-1 and C-3 on the first power path, be used for from preposition gear train to two planetary gear set transmitting torques.In this case, the outside friction disc support of clutch C-3 or cylinder side or piston side are connected with the first break B-1 with the pressure compensation side.And the inner attrition piece support of three-clutch C-3 is connected with the pressure compensation side with cylinder side or the piston side of first clutch C-1, and wherein, the inner attrition piece support of first clutch C-1 is arranged on outlet side and is connected with a sun gear of third planet gear train.
In addition, claimant's DE 199 49 507 A1 disclose a kind of multispeed manual transmission, wherein, have two not changeable preposition gear trains on the input shaft, produce two kinds of rotating speeds on the output terminal, except the rotating speed of input shaft, can switch like this by the selectivity closure of employed gearshift parts according to acting on the switchable compound planet gear group of output shaft selectively, be from a gear and switch to separately next higher or lower gear, only need connect or disconnect separately gearshift parts in two direct operated gearshift parts.
DE 199 12 480 A1 disclose a kind of can self-shifting automotive transmission, have the planetary gear set of three single connecting sheets and be used for six forward gears of switching and three breaks and two clutches that reverse gear, also have an input shaft and an output shaft.This can consist of by self-shifting automotive transmission like this, input shaft directly is connected with the sun gear of the second planetary gear set and input shaft can be connected with the sun gear of the first planetary gear set and/or by the connecting sheet of second clutch with the first planetary gear set by first clutch.As additional or select, the sun gear of the first planetary gear set is connected with the shell of speed changer by the first break and/or the connecting sheet of the first planetary gear set is connected with shell by second brake and/or the sun gear of third planet gear train passes through the 3rd break and is connected with shell.
In addition, DE 102 13 820 A1 disclose a kind of multistage automatic transmission, comprise the first input path T1 of the first variator drive ratio; Variator drive ratio is greater than the second input path T2 of this first input path T1; Planetary gear set with four parts wherein, is first component, second component, the 3rd parts and the 4th parts in the order of speed curves figure upper-part; The rotation of input path T2 is delivered to clutch C-2 on the first component S3; Be delivered to clutch C-1 on the 4th parts S2 with rotating from input path T2; Be delivered to clutch C-4 on the first component with rotating from input path T1; Be delivered to clutch C-3 on the second component C3 with rotating from input path T1; Produce the break B-1 of the 4th parts combination; Produce the break B-2 of second component combination; And output member that is connected with the 3rd parts R 3.
In the framework of claimant DE 101 15 983 A1, introduced a kind of multispeed manual transmission, have an input shaft that is connected with preposition gear train, an output shaft that is connected with rearmounted gear train and maximum seven gearshift parts, optionally switch changeable at least seven forward gears without the mixing connection by it.Preposition gear train can not be made of with the preposition planetary gear set that the first preposition planetary gear set is switched a preposition planetary gear set or maximum two, wherein, rearmounted gear train utilizes two switchable rearmounted planetary gear set to consist of as dual connecting plate four shaft transmissions and has four free axises.The first free axis of these dual connecting plate four shaft transmissions and the first gearshift parts are connected, and the second free axis and the second and the 3rd parts of shifting gears are connected, and the 3rd free axis and the 4th and the 5th parts of shifting gears are connected with the 4th free axis and are connected with output shaft.A kind of multispeed manual transmission with six gearshifts of total parts is proposed according to this invention, and the 3rd free axis of rearmounted gear train or the first free axis are additional to be connected with the 6th gearshift parts.Have the multispeed manual transmission that amounts to seven gearshift parts and propose according to this invention a kind of, the 3rd free axis additional with the 6th gearshift parts D ' be connected free axis and add with the 7th parts of shifting gears and be connected.
In addition, claimant's DE 101 15 987 A1 have introduced a kind of multispeed manual transmission with at least seven gears.This speed changer is comprised of not changeable preposition gear train and the switchable rearmounted gear train mode with dual connecting plate four shaft transmissions except input shaft and output shaft.Preposition gear train is comprised of the first planetary gear set, and it can also switch to selectively rearmounted gear train the second rotating speed is provided except the input speed that input shaft is provided.Rearmounted gear train is comprised of two switchable planetary gear set, and they utilize six gearshift parts can switch at least seven gears, wherein form two power paths.In this regard, in each shift process, avoid all the time mixing connection in the advantageous mode of tool.In addition, DE 29 14 969 discloses a kind of 9 gear multispeed manual transmissions; It comprises eight gearshift parts and four gear trains.
On the whole, the self shifter automotive transmission of planetary gear construction is existing in the prior art introduces in a large number and is continually developed and improve.Therefore these speed changers have the forward gear of sufficient amount and one and reverse gear, and have the very high total allocation of employing and favourable speed changer respectively keeps off the variator drive ratio that the speed ratio interval is highly suitable for automobile.In addition, these speed changers can make to have very high startup variator drive ratio and comprises direct gear on the direction of advance, and both has been applicable to Pkw and also is applicable to Nkw and uses.In addition, these speed changers need lower manufacturing spending, particularly the gearshift parts of lesser amt, and avoid dual connection in the situation that order is switched, thereby are switching in the situation about determining on the gear group separately an only gearshift of conversion parts.
Summary of the invention
The object of the invention is to, a kind of multispeed manual transmission that starts described type is provided, wherein, the efficient that manufacturing is paid wages and is optimized and travels and keep off raising master aspect traction and the engagement loss for this reason.And according in the multispeed manual transmission of the present invention, make low torque act on gearshift parts and planetary gear set and the rotating speed of axle, gearshift parts and planetary gear set is remained on the alap degree.In addition, need quantity and the speed changer of observing gear distribute, and realize that six forward gears and at least one reverse gear thereby can have the advantage mode.In addition, be suitable for using at the automobile of any structure according to speed changer of the present invention, be specially adapted to preposition line setting.
This purpose is achieved by the feature of claim 1 according to the present invention.The advantageous formation of other advantages and tool is from dependent claims.
Provide accordingly a kind of planetary gear construction according to multispeed manual transmission of the present invention, have an input shaft and an output shaft of being arranged in the shell.Be called below having in addition at least three planetary gear set of first, second, and third planetary gear set, at least six running shafts-below be called input shaft, output shaft, the 3rd, the 4th, the 5th and the 6th axle-and at least five gearshift parts comprising break and clutch, their selective binding make and produce different variator drive ratio between input shaft and the output shaft, thereby can realize that best six forward gears and one reverses gear.
In this case, input shaft is connected with the sun gear of the second planetary gear set all the time, can be connected dividually with the 4th axle with the 3rd axle and by another clutch by a clutch, wherein the 3rd axle is connected with the connecting sheet of the first planetary gear set all the time, be connected on the shell and by a clutch by a break and can be connected dividually with the 6th axle, wherein the 4th axle is connected with the sun gear of the first planetary gear set all the time and is connected on the shell by a break.
The 5th axle is connected connecting sheet with the internal gear of the first planetary gear set all the time and is connected with the third planet gear train in addition, and wherein the 6th axle is connected with the internal gear of the second planetary gear set all the time.
According to the present invention output shaft all the time with the internal gear of third planet gear train be connected the connecting sheet of planetary gear set and be connected, wherein the sun gear of third planet gear train is connected on the shell by non-rotatable axle is anti-with turning round.
Produce a kind of total allocation that is specially adapted to the variator drive ratio of car and has obviously improved multispeed manual transmission by this multispeed manual transmission according to formation of the present invention, improved thus driving comfort and greatly reduced consumption.
In addition, utilize according to multispeed manual transmission of the present invention by reducing the quantity of gearshift parts best two breaks and three clutches and obviously reduced and made spending.Utilize according to multispeed manual transmission of the present invention and can the advantageous mode of tool adopt fluid torque converter, fluid clutch, outside startup clutch or also can adopt other applicable outside activation member to start.Also it is contemplated that to adopt with the whole activation member that consists of of speed changer and carry out start-up course.Preferably be applicable to a kind of gearshift parts in the first forward gear and the manipulation of reversing gear.
In addition, in the gear high efficiency relevant with the engagement loss with traction of travelling according to a kind of master of multispeed manual transmission formation of the present invention.
In addition, exist low torque on the gearshift parts of multispeed manual transmission and the planetary gear set, reduce wearing and tearing on this multispeed manual transmission in the advantageous mode of tool thus.In addition, corresponding little size be can also produce by low torque, required structure space and corresponding cost reduced thus.In addition, on these axles, gearshift parts and planetary gear set, also exist the slow-speed of revolution.
In addition, design like this according to speed changer of the present invention, make no matter it is all can to combine from different power train structures on the power transmission direction or aspect the space.
Description of drawings
The present invention is described in detail for example by accompanying drawing for the below.Wherein:
Fig. 1 illustrates the schematic representation of a foundation multispeed manual transmission preferred implementation of the present invention; And
Fig. 2 illustrates the schematic representation of shifting gears for example according to multispeed manual transmission of the present invention according to Fig. 1.
Embodiment
Fig. 1 illustrates a foundation multispeed manual transmission of the present invention, has the input shaft 1 (An) and the output shaft 2 (Ab) that are arranged in the shell G.Have three planetary gear set P1, P2, P3, they are preferably as negative planetary gear set formation and by being set in sequence in of P1, P2, P3 axial upper (equally on the power transmission direction).
As seeing from Fig. 1, only have five gearshift parts, i.e. two breaks 03,04 and three clutch 13,14 and 36.Utilize these gearshift parts can realize best six forward gears and a selectivity gearshift of reversing gear.Have six running shafts, the i.e. axle 1,2,3,4,5 and 6 of total according to multispeed manual transmission of the present invention.
In the multispeed manual transmission of foundation Fig. 1, carry out transmission by axle 1 according to the present invention, this axle is connected with the sun gear of the second planetary gear set P2 all the time, can be connected dividually with axle 4 with axle 3 and by clutch 14 by clutch 13, its axis 3 is connected with the connecting sheet of the first planetary gear set P1 all the time, be connected to shell G by break 03 and upward and by clutch 36 can be connected dividually with axle 6, its axis 4 is connected with the sun gear of the first planetary gear set P1 all the time and is connected on the shell G by break 04.
This outer shaft 5 is connected connecting sheet with the internal gear of the first planetary gear set P1 all the time and is connected with third planet gear train P3, its axis 6 is connected with the internal gear of the second planetary gear set P2 all the time.
Transmission is undertaken by axle 2, this axle 2 all the time with the internal gear of third planet gear train P3 be connected the connecting sheet of planetary gear set P2 and be connected.The sun gear of third planet gear train P3 is prevented being connected on the shell G by axle 0 with turning round in addition.
In this case in the framework of illustrated embodiment, clutch 13 and 14 end on observation on the power transmission direction by 13 and 14 be set in sequence in the first planetary gear set P1 front and can be used as lamella clutch and have a shared outside friction disc support.Break 04,03 same end on observation on the power transmission direction with 04,03 the front that is set in sequence in the first planetary gear set P1.
Layout on the gearshift space of components can be the restriction that is subjected to arbitrarily and only size and external environment condition.
Fig. 2 illustrates the schematic representation of shifting gears for example according to multispeed manual transmission of the present invention according to Fig. 1.Be closed two the gearshift parts of each gear.Can find out that from this gearshift schematic representation the separately variator drive ratio i of single gear for example and the speed changer of therefrom determining respectively keep off speed ratio interval phi.Planetary gear set P1, P2, the P3 fixedly exemplary value of variator drive ratio are respectively-3.250 ,-2.282 or-2.480.Can find out from this gearshift schematic representation in addition, in order gearshift situation, avoid dual connection or mix connecting, because two adjacent gears utilize gearshift parts jointly.The 4th gear consists of preferably as directly keeping off in this case.
The first gear keeps off by closed clutch 14 and 36 by closed break 04 and clutch 36 and the 3rd and producing by closed break 03 and clutch 36, the second gear.In addition, the 4th gear produces by closed break 04 and clutch 13 by closed clutch 13 and the 14 and the 6th gear by closed clutch 13 and clutch 36, the 5th gear.As from seeing the gearshift schematic representation, reversing gear produces by closed break 03 and clutch 14.
According to the present invention, startup can utilize the whole gearshift parts 03,36 that consist of to carry out (IAK), wherein, and to this particularly suitable required break 03 at the first forward gear and on reversing gear in two kinds of mode of executions.In addition, in identical transmission schematic representation, also can produce different trip stopping according to the gearshift logic, thereby can form the scheme of a kind of purposes special use or automobile specified.
Can have additional free wheel device in any suitable position of multispeed manual transmission for this reason, for example be connected with two axles between an axle and shell or when needing.
On input side or outlet side, according to the present invention an axletree differential mechanism and/or a distributor differential mechanism can be set.
In the framework of the advantageous further formation of a kind of tool, input shaft 1 can separate with the active motor as required by link, wherein, can use fluid torque converter, hydraulic coupling, dry type starting clutch, dry-type start-up clutch, magnetic powder clutch or centrifugal clutch as link.This activation member also can be arranged on the power transmission direction of speed changer back, and wherein, input shaft 1 is connected with the bent axle of motor all the time in this case.
In addition a torsional vibration damper can be set between motor and speed changer according to multispeed manual transmission of the present invention.
In the framework of the unshowned another kind of mode of execution of the present invention, on each axle, break without wearing and tearing can be set on preferred input shaft 1 or the output shaft 2, for example as hydraulic pressure or electronic exhaust brakes or this class break, this point has the meaning of particular importance concerning the application on commerial vehicle.In addition, can on each axle, preferably have auxiliary drive at input shaft 1 or output shaft 2 for the additional unit of transmission.
Employed gearshift parts can be used as the load solenoidoperated cluthes or break consists of.Particularly can make the clutch or the break that firmly cooperate, for example lamella clutch, band brake and/or cone clutch.In addition, also can use break and/or the clutch of form fit as the gearshift parts, for example as synchronizer or jaw clutch.
Another advantage of multispeed manual transmission described here is, on each axle as generator and/or all can mounted motor as drive unit.
Self-evident; any structural formation; particularly no matter the setting on planetary gear set and any space of gearshift parts is itself and needs only each other and thus technical rational; all be under the protection domain of this claim; and do not affect the function of speed changer cited in the claim, even consisting of in the accompanying drawings not clear and definite or the specification, these list.
Reference character
0 axle
1 axle
2 axles
3 axles
4 axles
5 axles
6 axles
03 break
04 break
13 clutches
14 clutches
36 clutches
The P1 planetary gear set
The P2 planetary gear set
The P3 planetary gear set
The An input
Ab output
The i variator drive ratio
The phi speed changer respectively keeps off the speed ratio interval
The G shell
Claims (27)
1. the multispeed manual transmission of planetary gear construction, comprise: at least six revolvable axles (1,2,3,4,5,6) comprise the input shaft (1) that is arranged in the shell (G) and an output shaft (2), the 3rd axle (3), the 4th axle (4), the 5th axle (5), the 6th axle (6); Three planetary gear set (P1, P2, P3) comprise the first planetary gear set (P1), the second planetary gear set (P2), third planet gear train (P3); And at least five gearshift parts (03,04,13,14,36), comprise the first break (03), second brake (04) and first clutch (13), second clutch (14), three-clutch (36), their selective binding make and produce different variator drive ratio between input shaft (1) and the output shaft (2), thereby can realize that at least six forward gears and one reverses gear, wherein, input shaft (1) is connected with the sun gear of the second planetary gear set (P2) all the time, can be by first clutch (13) with the 3rd axle (3) and can be connected dividually with the 4th axle (4) by second clutch (14), wherein the 3rd axle (3) is connected with the connecting sheet of the first planetary gear set (P1) all the time, energy is connected to shell (G) upward by the first break (03) and can be connected dividually with the 6th axle (6) by three-clutch (36), wherein the 4th axle (4) is connected with the sun gear of the first planetary gear set (P1) all the time and can be connected on the shell (G) by second brake (04), wherein the 5th axle (5) is connected P3 with the internal gear of the first planetary gear set (P1) all the time with the third planet gear train) connecting sheet be connected and the 6th axle (6) is connected with the internal gear of the second planetary gear set (P2) all the time, wherein output shaft (2) all the time with the internal gear of third planet gear train (P3) be connected the connecting sheet of planetary gear set (P2) and be connected, and wherein the sun gear of third planet gear train (P3) is connected on the shell (G) by the 7th axle (0) is anti-with turning round.
2. by multispeed manual transmission claimed in claim 1, it is characterized in that described multispeed manual transmission is the automatic transmission of automobile.
3. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that, planetary gear set (P1, P2, P3) set gradually in the axial direction by the order of the first planetary gear set, the second planetary gear set, third planet gear train or the power transmission direction on.
4. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that planetary gear set (P1, P2, P3) consists of as negative planetary gear set.
5. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that first clutch (13) and second clutch (14) end on observation are in the front that be set in sequence in first planetary gear set (P1) of power transmission direction by first clutch (13), second clutch (14).
6. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that first clutch (13) and second clutch (14) have a shared outside friction disc support as lamella clutch.
7. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that second brake (04) and the first break (03) end on observation are in the front that be set in sequence in first planetary gear set (P1) of power transmission direction by second brake (04), the first break (03).
8. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that, can realize six forward gears, wherein the first gear is by closed the first break (03) and three-clutch (36), the second gear is by closed second brake (04) and three-clutch (36), the 3rd gear is by closed second clutch (14) and three-clutch (36), the 4th gear is by closed first clutch (13) and three-clutch (36), the 5th gear is by closed first clutch (13) and second clutch (14) and the 6th gear passes through closed second brake (04) and first clutch (13) produces.
9. by multispeed manual transmission claimed in claim 8, it is characterized in that reversing gear produces by closed the first break (03) and second clutch (14).
10. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that, can use additional free wheel device in any suitable position.
11. by multispeed manual transmission claimed in claim 10, it is characterized in that between described at least six revolvable axles (1,2,3,4,5,6) and shell (G), having free wheel device.
12., it is characterized in that having input device and output unit in the identical faces of shell by claim 1 or 2 described multispeed manual transmissions.
13. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that axletree differential mechanism and/or distributor differential mechanism are arranged on input side or the outlet side.
14. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that input shaft (1) can separate with the active motor by link.
15. by the described multispeed manual transmission of claim 14, it is characterized in that fluid torque converter, hydraulic coupling, response time clutch, dry-type start-up clutch, magnetic powder clutch or centrifugal clutch can be set to link.
16. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that the power transmission direction in the speed changer back arranges an outside activation member, wherein, input shaft (1) is fixedly connected with the bent axle of motor.
17. by the described multispeed manual transmission of claim 16, it is characterized in that described outside activation member is link.
18. by the described multispeed manual transmission of claim 17, it is characterized in that fluid torque converter, hydraulic coupling, response time clutch, dry-type start-up clutch, magnetic powder clutch or centrifugal clutch can be set to link.
19., it is characterized in that the gearshift parts (03,36) that start by speed changer carry out by claim 1 or 2 described multispeed manual transmissions, wherein, input shaft (1) is connected with the bent axle of motor all the time.
20. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that, a torsional vibration damper be set between motor and speed changer.
21. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that, the break without wearing and tearing all be set on each axle.
22. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that, on additional each axle of unit of transmission auxiliary drive being set all.
23. by the described multispeed manual transmission of claim 22, it is characterized in that auxiliary drive can be arranged on input shaft (1) or the output shaft (2).
24., it is characterized in that the gearshift parts consist of as load solenoidoperated cluthes or break by claim 1 or 2 described multispeed manual transmissions.
25. by the described multispeed manual transmission of claim 24, it is characterized in that, can use lamella clutch, band brake and/or cone clutch.
26. by claim 1 or 2 described multispeed manual transmissions, it is characterized in that break and/or the clutch of form fit are set to the parts of shifting gears.
27., it is characterized in that the energy mounted motor is as generator and/or as drive unit on each axle by claim 1 or 2 described multispeed manual transmissions.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102006006616.2 | 2006-02-14 | ||
| DE102006006616A DE102006006616A1 (en) | 2006-02-14 | 2006-02-14 | Multi-step gear for planetary transmission e.g. automatic gearbox for motor vehicle, has three planetary sets, six rotational shafts and five shift elements |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101021255A CN101021255A (en) | 2007-08-22 |
| CN101021255B true CN101021255B (en) | 2013-02-13 |
Family
ID=38319603
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200710005337.1A Expired - Fee Related CN101021255B (en) | 2006-02-14 | 2007-02-14 | Multi-gear transmission |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US7507179B2 (en) |
| CN (1) | CN101021255B (en) |
| DE (1) | DE102006006616A1 (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006006638A1 (en) * | 2006-02-14 | 2007-09-06 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE102006006642A1 (en) * | 2006-02-14 | 2007-08-23 | Zf Friedrichshafen Ag | Planetary gear for multi-speed transmission in vehicle, has shift unit with brakes and clutches, whose selective intervention at different gear tooth ratio operates between drive shaft and output shaft |
| US8016715B2 (en) * | 2009-01-16 | 2011-09-13 | GM Global Technology Operations LLC | Multi-speed transmission having three planetary gear sets |
| DE102009001253B3 (en) * | 2009-03-02 | 2010-06-24 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US8257219B2 (en) * | 2009-07-16 | 2012-09-04 | GM Global Technology Operations LLC | Multi-speed transmission having three planetary gear sets |
| US8425372B2 (en) * | 2010-07-14 | 2013-04-23 | Hamilton Sundstrand Corporation | Geared turbofan emergency power |
| DE102012212257A1 (en) * | 2011-09-27 | 2013-03-28 | Zf Friedrichshafen Ag | planetary gear |
| JP5736406B2 (en) * | 2013-04-03 | 2015-06-17 | 本田技研工業株式会社 | Control device for automatic transmission |
| CN103511565A (en) * | 2013-10-17 | 2014-01-15 | 中国北方车辆研究所 | Automatic six-gear planetary transmission |
| CN104033545B (en) * | 2014-06-11 | 2016-05-18 | 同济大学 | Six shift transmissions |
| KR101916063B1 (en) * | 2016-09-12 | 2018-11-07 | 현대자동차 주식회사 | Planetary gear train of automatic transmission for vehicles |
| CN108528185B (en) * | 2018-06-07 | 2024-01-19 | 精进电动科技股份有限公司 | Longitudinally-arranged multi-gear electric driving power assembly |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4395925A (en) * | 1979-09-13 | 1983-08-02 | Daimler-Benz Aktiengesellschaft | Planetary gear change-speed transmission |
| CN1043373A (en) * | 1988-12-12 | 1990-06-27 | 刘大刚 | Multi-gear gearbox with free-wheel coupling |
| EP0434525A1 (en) * | 1989-12-18 | 1991-06-26 | Pierre André Georges Lepelletier | Multispeed automatic transmission for vehicles |
| DE19949507A1 (en) * | 1999-10-14 | 2001-04-19 | Zahnradfabrik Friedrichshafen | Multi-stage transmission |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4144106B2 (en) | 1998-12-21 | 2008-09-03 | アイシン・エィ・ダブリュ株式会社 | Automatic transmission for vehicles |
| DE19912480B4 (en) | 1999-03-22 | 2006-03-16 | Zf Friedrichshafen Ag | Automatically switchable motor vehicle transmission |
| JP4438247B2 (en) | 2001-03-29 | 2010-03-24 | アイシン・エィ・ダブリュ株式会社 | Automatic transmission for vehicles |
| DE10115987A1 (en) | 2001-03-30 | 2002-10-02 | Zahnradfabrik Friedrichshafen | Multi-speed transmission |
| DE10115983A1 (en) | 2001-03-30 | 2002-10-10 | Zahnradfabrik Friedrichshafen | Multi-speed transmission |
| US7303500B2 (en) * | 2005-12-16 | 2007-12-04 | Ford Global Technologies, Llc | Multiple-speed automatic transmission |
| US7396305B2 (en) * | 2006-02-21 | 2008-07-08 | Gm Global Technology Operations, Inc. | Electrically variable transmission having three planetary gear sets, a stationary member and three fixed interconnections |
-
2006
- 2006-02-14 DE DE102006006616A patent/DE102006006616A1/en not_active Withdrawn
-
2007
- 2007-02-09 US US11/705,074 patent/US7507179B2/en not_active Expired - Fee Related
- 2007-02-14 CN CN200710005337.1A patent/CN101021255B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4395925A (en) * | 1979-09-13 | 1983-08-02 | Daimler-Benz Aktiengesellschaft | Planetary gear change-speed transmission |
| CN1043373A (en) * | 1988-12-12 | 1990-06-27 | 刘大刚 | Multi-gear gearbox with free-wheel coupling |
| EP0434525A1 (en) * | 1989-12-18 | 1991-06-26 | Pierre André Georges Lepelletier | Multispeed automatic transmission for vehicles |
| DE19949507A1 (en) * | 1999-10-14 | 2001-04-19 | Zahnradfabrik Friedrichshafen | Multi-stage transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| US20070202983A1 (en) | 2007-08-30 |
| CN101021255A (en) | 2007-08-22 |
| DE102006006616A1 (en) | 2007-08-30 |
| US7507179B2 (en) | 2009-03-24 |
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